Coil winding machine



July 7, 1959 A. GREINER 2,893,195

COIL WINDING MACHINE Filed June 17 1958 5 Sheets-Sheet 1 TURNS PER mguTURNS PER. mcH

SELECTOR 23 INVENTOR. 60mm @IZEWVEB.

BY FW A. GREINER COIL WINDING MACHINE 5 Sheets-Sheet 2 INVENTOR. flE/VOTeE/A ER July 7, 1959 Filed June 17, 1958 y 7, 1959 A. GREINER I2,893,195

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/777UE/VEY- July 7, 1959 A. GREINER COIL WINDING MACHINE 5 Sheets-Sheet4 Filed June 17, 1958 J a m 1 4% K k 0 1 6 w O Q 2/11 0 1 o 3 5 m 0 5 44 4 a A a INVENTOR. flz,v0 aka/v52 y 7, 1959 A. GREINER 2,893,195

COIL WINDING MACHINE Filed June 17, 1958 5 Sheets-Sheet 5 States Patent2,893,195 com WINDING MACHINE I Arno Greiner, 'Irvington, N.J., assignorto Uwimco, Inc., Springfield, N.J., a corporation of New JerseyApplication June 17, 1958, Serial No. 742,675 12 Claims. (Cl. 57-3) Thisinvention relates to coil winding machines and more particularly tomachines which wind a coil on a continuously fed mandrel. i

The coils made by the present invention are predominatingly' used asfilaments for lamps, and it is consequently of great importance that thewinding shall be uniform and made precisely witha predetermined numberof convolutions or turns of filament per unit length of the mandrel.Heretofore attempts have been made to attain the specified number ofturns by calculation of gear ratios determinative of the advancement ofthe mandrel in its relationto the number of revolutions of the windinghead. Even with the most careful calculations and construction, thepriorart machines often fail to produce the intended and. desired accuracy.Furthermore, in the prior art machines it is necessary to laboriouslychange the gears or, t.p.i. drums (abbreviation used in the trademeaning turns per inch) in order to obtain any change from a fixednumber of convolutions of filament produced by the machine to any. othernumber of convolutions.

Basically, the present invention proposes a machine wherein extremelyaccurate precision of number of convolutions per unit length of themandrel can be readily accomplished.

Of similar nature, the .invention proposesa construction permitting bothadjustment and large change of the numbertof convolutionsby a readilymanipulated means underoperator control, and. without requiringpresent-day elaborate calculations, or in fact, without requiring anycalculations by the. operator or any mechanical replacement of gears ordrums.

More specifically, the invention provides a machine wherein minute orother adjustment as 'well as large change of the convolutions per unitlength of mandrel by direct reference thereto and by implication fromthe context.

Referring to the accompanying drawings, in which like numerals ofreference indicate similar parts throughout the several views; 1

Figures 1 and 2 are side elevations of a machine, looking at oppositesides thereof, incorporating the present invention;

Figure 3 is a front elevation of the machine;

. Figure 4 is an enlarged fragmentary portion of the dial control forsetting the turns per unit length on the mandrel;

Figure 5 is a sectional view on line V--V of Fig. 7;

Figure 6 is a sectional view on line VI-V1 of Fig. 5;

Figure 7 is a sectional view on line VII-VII of Fig. 5;

Figure 8 is a sectional view on line VIII-VIII of Fig. 5;

Figure 9 is a sectional view on line IX -IX of Fig. 5;

Figures 10 and 11 are corresponding sectional views on lines X-X andXI-XI respectively of Fig. 9;

Figures 12, 12a and 12!) are diagrammatic Views showing three differentpossible settings for the actuating on line XIV-XIV of in said drawings,the general organization-of the ma-- chine provides a hollow casting orhousing 20 which contains essential portions of the mechanism, and onthe outside of which a spool 21 containing a supply of mandrel wire 22may be mounted upon a shaft 23 that extends from side to side of thehousing and projects at one side to receive said spool 21, and projectsat the other side to receive a reel 24 on which the finished prodnot iswound. At the top of said housing 20 is provided a Winding head 25 whichis carried by and rotates with a tubular shaft identified in the tradeas the winding spindle 26, parallel to the spool and reel shaft 23. The

justment or change just referred to above, to .be made i with themachine in motion or not in motion, and re-" quires no materialdelay inproductivetoperation of the.

machine.

improved means obtaining forward motion only thereof and completelyeliminating detrimental occurrences of hesitation thereof heretoforecaused by gear back-lash and similar mechanical deficiencies.

In conjunction with the foregoing last-recited object, the inventionalso provides for applying desired tension in the mandrel wire-both infeeding the same to the coil winding head and in subsequent travelthereof to the reel on which the coil, with its mandrel, is wound.

A further important consideration of the invention is provision of onethat is usable for winding a selected one of various sizes of coil wireon a selected one of various sizes of mandrel wires, thereby providing amachine of universal character. I a

The invention also in'corpora'tes an improved spreader appropriatesheaves and another t.p.i. drum and thence to the reel 24 under guidanceof tracking mechanism 27 so as to be evenly wound in sequentially closeconvolutions and in successive layers on said reel.

For descriptive purposes, the winding head 25 includes a winding frame28 which revolves with the spindle 26 around the axis thereof and may beconsidered at this stage of the description as operating at a constantrate and therefore the number of turns or convolutions of the coil uponthe mandrel will be varied only by varying the forward rate of travel ofthe mandrel wire. An essen- 'tial feature of the present invention isprovision of a An electric motor 29 mounted at the top of the hous- 4ing 2!) proximate to what is herein termed the rear end of the machine,provides the actuating motive power, through a belt 30 and appropriatepulleys 31, 32 to a drive shaft 33 located'near the top; of: the;honslinrapproximately midway from front to. rear thereofand parallel toaforementioned shaft 23 and spindle 26; Said;

drive shaft 33 rotates at the selected ratingof the motor at. a constantspeed and continuously-while themachine; is, in operation, but; toaccommodate operation withdifferent sizes of wire, I prefer to'use atwo-speed motor so as to use the machine either with one or the other;

of the selected speeds. Drive shaft 33 is-shown projecting at one side,here termed the; left side, of the housing, and there carries the beltpulley 32 in fixed position,

thereon so as to be driven thereby, Next to that pulley,

and meunted in the proximate wall of the housing vis. av

bearing 34 for the shaft 33 and within the-housingtis a fixed frame '35providing, interalia, two other and spaced apart bearings-36, 36.; Fixedon said-drive shaft, between housing bearing 34-and; the most proximateof. frame:

bearings 36 are two adjacent drive gears which maybe distinguished bycalling them respectively small drive gear: 37 and large drive gear 38and constitute selective drive for speed; ofdrive. for theabove-mentioned winding head 25 which will be hereinafter more fullydescribed; Between the; pair of spaced apart bearings 36,

36 a worm 39 is fixed on said drive shaft 33. The small andlargedrive.gears 37, 38 and the worm- 39 accordingly will be subject to theselected speed'of themotor, and any change of-speed -of the motorreflects a corre-. sponding change of;speed of both of said drive gearsand of the worm.

Worm 39 meshes with a worm wheel 40 therebelow.

(seefigs. 6" and7) whichis mounted: upon what will be termed anintermedi te -shaft41 that extends from the worm Wheel in a directiontoward the rear of the housing and suitahlywjournaled in saidframe 35;At

the rear end of said intermediate shaft 41 is a bevelz.

gear 42 which is in, mesh with. a. driven bevel gear 43 on yetanothershaft 44 which for convenience in distinguish ing by terminology, willbereferred, to as 'theccam shaft since there, are two earns 45 thereontoward. oppositesides of thehousing from, driven bevel gear 43 as may.

beclearly seeninFig. 6. It will be understood that the camsha t; 44;andthe intermediate shaft 41. are axially in a common: horizontal plane andare entirely within. the .housingand with the cam. shaft parallel todrive shaft 33 andv in constant rotation. from said drive shaft.

General mention hasrbeen made hereinbefore that the mandrel wire passesaround appropriate t.p.i. drums.

More specifically, it may now. be stated that at the leftorfeeding sideof the machine there is a multiple-groove jacent thereto with. the.wirefrorn one groove-- of thedrurn-going around the idler-and then backto another groove'of .the t.p.i. drum, making at least partialconvolutions. in selected grooves of the drums so as to be positivelydriven and controlledin speed by said drums. T.p .i. drurns 46and 47areboth ofthe same diameter and are-mounted on opposite ends of a drumshaft 49- that. extends through the housing 20 and projects at the sidesthereof-near the front end. Said'drum shaft 49 is at about thesame-levelas and parallel to afore-mentioned'cam-shaft 44 which is nearthe rear end of the housing so that said shafts have considerabledistance between them.

The outstanding feature of the present invention comprises. means foreffecting-continuous steady drive for said t.p.i. drum shaft 49 from thecam shaft 44, but with capability of adjusting or altering the speed ofthe drum 1 therefrom at thec-sidepofv the-.lever:

dewnriina-zthehousihgthan.'theclevel'ofiithe cam shaft 44: andrdru'rrrshaft .49 :andihas. a general directio'mfrom front shaft.v while the camshaft continucsatits previousspeed. It has been stated that there aretwo cams 45 on the cam shaft, and now it maybe said that there are twogears 50 rotatably journaled on the drum shaft 49, and for reasons thatwill presently appear, these may be termed oscillating gears. Each ofsaid oscillating gears has a one-way clutch 51 (see Figs. 6, and 9 to11) connecting it to the drum shaft-49so thatwhenan oscillating gear 50rotates in one direction it will actuate the drum shaft, but ,when the:gear, oscillates; inathe: other direction the clutch thereforreleasesso' the. gear merely" rotates on said drum shaft without thenvactuatingit. One of said oscillating gears is driven by one of the earns45 and the other of said.oscill'ati'ng v gears. is driven by the otherone of the cams.

The driving connections for the oscillating gears is the sameconstruction for each, so description of one Will-orifice fonbotll:Generally speaking, thetsaid driving connection is ilrthe natureofsafwalking-beam. andaccords ingly comprises a lever 52whiclrxisz'carriedibya-pivotrocl 53:1 transverse toi both; levers; and:located; medially between; thei'oppositezendsgofrthex levers="(see-'Figs.r..5. and 9'- 7 tall); Beyondrthe pivotal mouutingrofthe; lever,longitudina'lly' toward both ends, said lever-issbifurcateittherebyx-providingn;oppositely extending pairssof rails 54 conveniently keptfromnspreadingvby' end.:caps:.55. A slide, block. 5.6::iscarriedeibetween each: pair; ofi-rails; so there. will -be one block at.onezlever. portion: beyon'dtthet pivot 53, toward; the frontofthe;.housing and: another. block atthe-oppositesiderof'the-pivotinnthe:other end portiongof -the levertoward the rearzofthe; housing; Each slide block-s56 has a;. pivot-pinSCI-projecting.- laterally. Said-:lever islowen to. -re'ar; of; said;housing, so; the; CHdS':LOfi= said lever are located more. .or. lessbeneath: said's shafts.

Associatedrwith. each cam-45, is .a rocker 58 pivoted 3.13159 toframe35: and-.jhavingJan. arm 62 :at the side of the. cam withascam-follower 670:. riding in thecam groove 61. That groove has acontour such that for partof. the :rotation of the cam, here ashownasone quadrant and designated-the inactiveportion ofithe complete ro--tative cycle,=. ityactuates therrocker on areturn swing,

whereasanother andimuchi longer portion ofthecamgroove 61,, here shown,asthree quadrants and designated theu active portion. Ofith'. complete.rotation; hasia con-- tour which applies anadvancing: orrrdrivingractuation to swing the rocker in a'direction opposite-tosaid returnswing. By this construction,theactuationofone rockerin. the; returnportion of its swinging. cycle-Willi prevail during-pa. part only .ofthe activerordriving portion of the cycleof. swing ofth'e other rocker,-and vieeversar Each:rocker. 58has an arm 63' projecting from: the pivot5-9h-away from. both-said :pivot. and cam, and: according tothe presentshowing that: arm 63, whichis'-more or less: horizontal, has adownward'driving -stroke"or swing due'=to;its cam (see Fig. 10) during-and inexcess of the interval that the corresponding arm 63 of the-otherrocker'58 is on upwardlinactiveor returnportion of its swing-under actuationfrom-ifsrcam: Thus at all times,

one or. the other of 'said horizontal-1y proje'cting arms 63isuoperating ina downwardor driving direction, and each with-saidgear-segment 64st): that-as the gearsegment" oscillates up and'downunder influence of the cam rocking the rocker, said rack'will have" acorrespondingup and downbut guided straight-line.longitudinal motion.Said rack depends at the side of the afore-mentioned bifuirted lever 52proxi'ma te to block 56and is trunnioned connection. therewith by pivotpin 57 projecting from said .blojck into said rack. Thus swing of therocker imparts swinging actuation for said walking-beam lever 52.

- The other block 56 in the other. end portion of said lever 52 makestrunnioned connection by its pivot pin 57 with another rack 66 whichalso is vertically and slidably mounted to have straight-linelongitudinal movement in the frame. There is, of course, a differentrack 66 for eaohlever, and each is in mesh with a respective one ofaforementioned oscillating gears 50. Cylinder 67 of the respectiveclutch 51 is fixed with respect to its oscillating gear, whereas theinternal rotor 68 ,of both of the clutches are fixed on the drum shaft49. The rotors have tapered pockets 69 next to the cylinders, andtherein are rollers 70 which ,frictional ly wedge betweenthe rotor andcylinder when the cylinder rotates in one direction and release when thecylinder rotates in the other direction. This or any suitable type ofoneway clutch may be employed, and by use thereof the clutches will eachfunction to rotate the drum shaft upon upward movement of the rack 66 inmesh with and oscillating the respective oscillating gear 50. Downwardmovement of the rack 66 consequently applies no driving impetus to thedrum shaft, and this inactivity occurs during the functioning of theabove-described inactive or return portion of the swing of thecorresponding rocker 58. The overlap of driving strokes of said rockersalso applies to the oscillating gears, so said drum shaft is drivenwithout intermission. It may now be said, furthermore, that the camgroove contours are such that theimparted rotation of the oscil- Zlatinggears during the active or driving direction of oscillation applies aconstant or even rate of movement :thereto so that the drum shaft has asmooth constant rate of rotation for any given setting of thespeed-regulating mechanisms as well as for the selected speed of themotor.

One speed changing mechanism is a selective drive at either one or twospeeds for the winding head obtained by utilization of large drive gear38 meshing with a small gear 71 on tubular shaft or spindle 26, or byutilization of small drive gear 37 in mesh with a large drive gear 72 onsaid spindle 26. These two gears 71 and 72 on the spindle are on acommon hub 73 slid-ably splined on said spindle and will be referred toas the small and large shift gears respectively. The hub 73 spaces theshift gears laterally far enough apart so that only one at a time canmesh with its respective drive gear, the spacing also being sufiicientto accommodate both of the driving gears between and free from the shiftgears for a neutral or non-driven location. A suitable gear-shiftmechanism is provided, and as here shown, a yoke 74 rides in acircumferential groove in hub 73 and projects upwardly to and secured ona slide rod 75 that extends parallel to the spindle to one side of themachine where it has a run 76 fixed thereon and to another rod, herecalled lockrod 77, parallel to and above slide rod 75. The rung 76 has aknob 78 at its outside for ease of manipulation. The lock-rod has threenotches 79 at its upper side for receiving a latch 80 to hold saidlock-rod in any one of three positions. The spacing of the notches ismade to correspond to the proper movement of the shift gears to causeeither one to register with its driving gear or to straddle both inneutral or non-driven position. There is thus a choice afforded ofdifferent rates of speed for rotating spindle 26, and as the windinghead 25 is on that spindle, the choice of speed will determine thenumber of coils produced per rotation of the drive shaft.

It may here be noted that the winding head 25 provides a face-plate 81fast on the spindle 26 so as to be rotated at the selected speed.Outwardly beyond the face plate 81 the hollow shaft projects far enoughto rotatably carry thereon the bobbin of filament or wire to be woundonto the mandrel wire. Said bobbin is designated by numeral 82 and thewire therefrom by numeral 83. Projecting from, the face-plate 31 iswinding frame 28 having guiding pulleys 8 4, 85 thereon for guidingpassage of the wire 83 off of the reel and back down to the mandrel. Asthe frame revolves around the mandrel, coiling of wire 83 around themandrel will be effected. This or any suitable winding head may beemployed.

The important speed-changing mechanism featured in the present inventionis one affecting the speed of travel of the mandrel wire at the selectedspeed of winding the filament coils therearound. In other words, thefaster the mandrel wire feeds, the less number of filament coils will bewrapped around it per unit length of the mandrel wire, and vice versathe slower the mandrel wire moves, the greater will be the number offilament coils wrapped around it, on the premise of course that thecoiling continues at the same selected speed. This speed changingmechanism is for the purpose of effecting change of speed of the mandrelwire only, and the range of change is such that the number of filamentcoils per unit'of length of the mandrel may be greatly. increased ordiminished if desired, or may be changed only slightly for preciseadjustment of coils per unit length. This change and/or adjustment ofspeed of the mandrel is obtained by varying the length of lever-arms ofthe walking-beam lever 52 between pivot 53 thereof to the respectivepivots 57 of slide blocks 56 for racks 65 and 66. For this purpose,pivot rod 53 has both of its ends, as shown in Fig. 7, protruding fromthe sides of a carriage 86 riding in a trackway 87 that extends in thesame general direction as the lever toward the front and rear of thehousing, said trackways being formed as part of said frame 35 in thehousing.

It may now be observed that whereas the total distance along lever 52from one rack 65 to the other rack 66 always remains constant, theleverage length from the fulcrum of the lever to the respective racksmay be varied by shifting the lever pivot 52. It is also a fact that thecam 45 always produces the same stroke S to its associated rack 65 asdiagrammatically indicated in Figures 12, 12a and 12b. With the leverpivot 53 midway between the racks, both of said racks will have equalstroke, so that the stroke S of the second rack will then be an amountequal to S of the first rack, this condition being illustrated in Fig.12. By moving pivot 53 closer to the second rack 66, as in Figure 12 thestroke S produced in that rack will be less than the constant length ofstroke S of the first rack 65. Likewise when the lever pivot is movedfrom its midway position toward the first rack 65 as in Fig. 12b, theconstant stroke of that rack will produce a greater stroke S in thesecond rack. The variable distances of the lever pivot 53 to the pivotpins 57 that connect the lever to the first and second racks areindicated in Figure 10 as variables r and r respectively. When r isshortened, the second rack not only has greater stroke, but has toaccomplish that stroke in the same fixed time of the constant stroke ofthe first rack, and as a result the second rack has to move faster andthus will rotate the t.p.i. drum shaft 49 faster. When r is shortened,the second rack 66 has a shortened stroke and the rack moves slower anddrives the drum shaft correspondingly slower. As adjustment of r and rmay cover a wide range, the speed of the drum shaft may thus be changedminutely or greatly as desired and thereby obtain the correspondingchange in movement of the mandrel.

Adjustment for lengths r and r is placed conveniently under theimmediate control of the operator, so that should the count of number ofcoils per unit length of mandrel show a discrepancy from the desirednumber, the operator may make the change to the desired number in aquick and convenient manner without stopping the machine. In carryingout this feature of the invention, a horizontally disposed rack 88 isprovided atone side of carriage 86 next to the top thereof and has apinion 89 in mesh therewith which will be rotated by,

thexrack whenthe: carriage is niovedback andforth.

The pinion is ona vertical shaft 90 shown protruding" through'the: topof the housingandth'erehas abevelgear 91meshing withasimi'laribevelgear92'on a'hori- Zontal' shaft" 93 that: extends tothe.front'of'th'e machine' and on which is a dial 94-rotatable'. in a casing951 The casing hasan. opening.96 for viewing the dial and has" -asetline. 97 for reading. thesetting shownon'the dial.

The dial is shown as having severahscales'thereon,'.one of which wouldapply, for instance, atone speed of the two-speedmotorandanother scalefor the other speed of "the motor, and another scale would. apply forone location of the .gear shift and another scale for a differ entlocation of gear-shift.

Adjiisted movement of'the carriage .is effected by a worm v98 that.rotates .in a nut 99 fixed on the bottom offthe carriage- The wormprojects at the front of the housing, and appropriately retained fromlongitudinal taut to. the t.p.i. drumatthat side of the machine, and'for keeping the woundmandrel' taut inits approach to and winding uponits reel. Said shaft 23 isrotated in a direction to wind the woundmandrel on its. reel. and

therefore also in a direction which will tend. to wind;

the mandrel wire onto the spool, but the spool is adapted to rotate onsaid shaft permitting the wire to unwind therefrom. However,a.frictional engagement is maintained upon said spool so: as totake upany slack in the wire: as itfeeds to the t.p.i. drumt Morespecifically,the construction hereshown. comprises an arbor 1 rotatable: on saidspooland reel shaft.23 and having an outside -diameter appropriate toreceive the spool 21 thereon with. sufficient frictional contact so thatthe spool and arbor function as a unit. The inner end of the arbor has:aperipheral flange102 directedtoward an annular seat 103 fixed on: androtatable with said shaft 23. A friction washer 104is interposed betweensaidseat and flange and frictional engagement is maintainedv by a spring105 at. theou-ter end of the arbor held under compression by nutsv 106-von the end of the shaft. the unwinding, of the mandrel wire from thespool rotates the spool counter to: the direction of rotation of theshaft, any slack in'the wire is immediately taken up by counter rotationtransmitted to the spool from the shaft.

Similarly, at. the other end of the spool and reel shaft 23, is an arbor107. rotatable thereon and receiving the. reel. 24 frictionally thereon.A friction washer 103- is interposed between the inner end of thearborand an annular seat 109 fixed on and rotatable with said shaft 23.Frictional. contact of said Washer with the arbor and seat is maintainedby a spring 110 at the outer end of .the arbor heldunder. compression bynuts 111 on theend .of the shaft. The diameter of the reel ismadealarger than the t.p.i. drum 47 from which the. woundmandrelis-received, so the greater surface speed of the reel will keep thewound. mandrel under tension, slippage of the arbor on shaft 23accommodating the difference. It. mayherebe noted that the spool andreel shaft 23 is driven by a gear 112 on the cam shaft 44 in mesh withan idler gear. 113 in turn meshing with a driven gear 114 fixedon-thespool and reel. shaft 23.

Tracking mechanism for guiding the filament-wound mandrel onto-the reelwith the convolutions juxtaposed insequentialorder andsuccessive-layers, acquires itsmotivation, from 'therreel arbor'107vsothe: tracking will As here confornrto thexspeed tof-rotation of thereel. showngmthe reel arbor has amintegral'ring 115'at the 8.5.endthereof toward the housing and of: greater diameterthanthe-reel,-themuter periphery of thering 'having wornr threads 116thereon."- A worm wheel"117"(see Fi'g-. 3') meshes with sai wormthreads-and through the agency- 11 of a -vertical axle 118 at the upperend ofwhich is a gear 119 (-see -Fig, 6-) drives an idler 1211 ('Figs.6; l3 and l'4-)-' ingtur-n-im mesh with a gear 121 on a" vertical camshaft" 122, on which b'oth 'said gear andaa cam 1 23' are rotat able.Afri'ction engagement 1-24 is1 interposed between" said 'gear-1'2Iand'cam"1'23"by which the carn is-normally driven byrotation'of"thegear; The frictional engage---- ment 1-2'4= permitssetting the cam to proper position for starting the tracking at theproper part of the reel. The cam rides against an arm 1'25"pivoted nextto its rear end and swung toward 'the cam by a spring126.. A guidethroat constituted byi-two parallel and proxi m'aterollers 127 dependingfrom abracket 128 "at"the-- forwardly projecting end portionof said arm,is providedand as the wound mandr'ehpasses through said throat in' itsapproach to the reel, the gradual backand forth swing'of thearm willfeed the wound mandrel 1 with successive convolutions close to eachother. Pref erably the arm has a longitudinal slot 129 adjustablyreceivingga screw'130 which holds thebracket '1'28" on the arm, wherebythe amplitude of swing of the throat maybe made more or lessagreeable tothe requirements of the reel.

I claim: I

l. A coil winding machine comprising a tubular spin die, a revolvable:frame havinga path of rotation coaxial to said spindle, means forcontinuously advancing a man= drel through'said'spindle and out of aforward end thereof, a walking-beamactuatingsaid means, said frame.coiling a filament around saidmandrel where advancing from saidspindle, andmeans 'forshifting'the fulcrum of said walking-beam and"thereby varying the rate of advancement of said mandrel fromsaidspindle for there? by varyingthe number of coils of filamentapplied'to said" mandrelper'unit length of advancement of said mandrel.

2. A coil. winding machine comprising a tubular spin dle,arevolvable-framehaving a path of rotation coaxial" to said'spind'le',means for continuously advancing amandrel through said spindle and outofa forward end thereof,v a pair of walking-beams with overlapping strokesapplying continuous and constant rate ofactuation' to said means,saidframe coiling afilament around said mandrel where 'a'dvancing fromsaid spindle;and means for shift.- ing the fulcrums of saidwalking-beamsand thereby vary ing the'rate of advancement of said mandrel from said"spindle for thereby varying the number of coils of filament" applied tosaid mandrel perunit length of advancement of said mandrel;

3. A coil winding machine comprising a tubular spin-' die, arevolva'bl'e frame having a path of rotation coaxial tosaid'spindle,rotatingmeans for continuously advancing a mandrel throughsaid spindle and out of a forward end thereof, said frame coiling afilament around said i mandrel where advancingfromsaid spindle, aWalking beam, a first reciprocating member at one end portion of thewalking-beam always applying the same length of stroke thereto, asecond" reciprocating member at the other endportion of.said'walking-beam actuating said rotating means, said walking-beamhavinga fulclum betweensaid first'and second members, and means for shiftingthe fulcrum of saidwalking-beamv with respect to said" first and.second'members and thereby varying the rate of advancementof saidmandrel from said spindle for there-' by varying the number of coils offilament applied to said mandrel per unit length of advancement of saidmandrel;

4. A coil winding machinecomprising a'tubular spindle, a revolvableframe having'a path of rotation coaxial to-said spindleg rotatingmeansfor continuously'advancinga mandrel through'sai'd spindle and outof a forward end thereof, said frame coiling a filament around said"mandrel where advancing from said 'spindle; az pair of walking-beams, afirst reciprocating member at one end portion of one of the pair ofwalking-beams and another first reciprocating member a; a correspondingend portion of the other walking beam, both of said first members alwaysapplying the same length of stroke to its respective walking-beam, asecond reciprocating member at the other end portion of one of saidwalking-beams and another second reciprocating member at thecorresponding end portion of the other walking-beam, said secondreciprocating members successively actuating said rotating means, saidwalking-beams having a fulcrum between said first and second members,and means for shifting the fulcrum of said walking-beams with respect tosaid first and second members and thereby varying the rate ofadvancement of said mandrel from said spindle for thereby varying thenumber of coils of filament applied to said mandrel per unit length ofadvancement of said mandrel.

5. A coil winding machine in accordance with claim 4, wherein each ofsaid first reciprocating members is a slidable rack, and wherein thereare two cams and two oscillating gear segments respectively actuated bysaid cams, said gear segments each in mesh'with a respective one of saidracks for reciprocating the same.

6. A coil winding machine in accordance with claim 4, wherein each ofsaid second reciprocating members is a slidable rack, and wherein thereare two oscillating gears respectively in mesh with and actuated by saidracks, said gears each having a one-way clutch on a common shaft andsaid shaft having the afore-mentioned rotating means for continuouslyadvancing the mandrel mounted thereon.

7. A coil winding machine in accordance with claim 4, wherein each ofsaid first reciprocating members is a slidable rack, and wherein thereare two cams and two oscillating gear segments respectively actuated bysaid cams, said gear segments each in mesh with a respective one of saidracks for reciprocating the same, and wherein each of said secondreciprocating members is a slidable rack, and wherein there are twooscillating gears respectively in mesh with and actuated by saidlast-mentioned racks, said gears each having a one-way clutch on acommon shaft and said shaft having the afore-mentioned rotating meansfor continuously advancing the mandrel mounted thereon.

8. A coil winding machine in accordance with claim 7, wherein a slidablecarriage is provided carrying the fulcrum for said walking-beam, andwherein slide blocks are slidably mounted in said walking-beam and eachpivoted to a respective one of said racks whereby sliding said carriagevaries the length of lever arm of the walking-beam from the fulcrum toeach rack.

9. A coil winding machine in accordance with claim 7, wherein a slidablecarriage is provided carrying the fulcrum for said walking-beam, saidcarriage having a worm control for manually sliding the same, andwherein slide blocks are slidably mounted in said Walking-beam and eachpivoted to a respective one of said racks whereby sliding said carriageby operation of said worm varies the length of lever arm of thewalking-beam from the fulcrum to each rack.

10. A coil winding machine in accordance with claim 7, wherein aslidable carriage is provided carrying the fulcrum for saidwalking-beam, said carriage having a worm control for manually slidingthe same, and a dial connected with and responsive to sliding motionimparted by said worm control to said carriage.

11. A coil winding machine comprising a tubular spindle, variable speedactuating means for advancing a continuous mandrel through said spindleout of a forward end thereof, a gear-driven winding head proximate tosaid forward end of said spindle adapted to coil a filament around saidmandrel upon passage of the mandrel from said forward end of thespindle, a shaft adapted to mount a spool for feeding supply of mandreland to mount a reel for the wound mandrel, said shaft rotating in adirection tending to wind the mandrel back onto the spool and to windthe wound mandrel onto the reel, and means permitting slippage of thespool on the shaft for withdrawal of the mandrel from the spool.

12. A coil winding machine comprising a tubular spindle, variable speedactuating means for advancing a continuous mandrel through said spindleout of a forward end thereof, a gear-driven winding head proximate tosaid forward end of said spindle adapted to coil a filament around saidmandrel upon passage of the mandrel from said forward end of thespindle, a shaft adapted to mount a spool for feeding supply of mandreland to mount a reel for the wound mandrel, means permitting slippage ofthe reel with respect to the shaft, and tracking means for feeding thewound mandrel to said reel, said tracking means having a drivecoordinated to the rotation of the reel and its slippage.

References Cited in the file of this patent UNITED STATES PATENTS1,094,047 Ames Apr. 21, 1914 2,706,376 Kerr Apr. 19, 1955 2,815,638Curtiss et al. Dec. 10, 1957

